Compacting machine



4 Sheets-Sheet 1 Filed March 23, 1965 INVENTOR.

HENRY WAYER BY MAHONEY, MILLER 8 RAMBO ATTORNEYS June 27, H WAYERCOMPACTING MACHINE 4 Sheets-Sheet 2 Filed March 25, 1965 5 v 5 g M; 0 3WM A w y y my WM ooooo M 3, 5 Ma 0n 3: E w H H L W .a I W L g i:

W ma F m u .H u w- -3 J I L 3 A P 5 4 w 2 BY MAHONEY, MILLER 8 RAMBOJune 27, 1967 H. WAYER 3,327,598

COMPACTING MACHINE Filed March 23, 1965 4 Sheets-Sheet 5 2/ Q4 7/ t m/Z5 54 Fife laA ";5 5; V/ m j 52 31 2' 57 INVENTOR HENRY WAYER BY 2 5MAHONEY, MILLER a RAMBO ATTORNEYS June 27, 1967 WAYER 3,327,598

COMPACTING MACHINE Filed March 23, 1965 4 Sheets-Sheet 4 INVENTOR. HENRYWA YE R BY MAHONEY, MILLER 8 RAMBO MI I ATTORNEYS United States Patent3,327,598 COMPACTING MACIHNE Henry Wayer, 960 S. Champion Ave, Columbus,Ohio 43206 Filed li Iar. 23, 1965, Ser. No. 442,124 17 Claims. (Cl.94--48) My invention relates to a compacting machine. It has to do, moreparticularly, with a wheeled vehicle which is adapted to move overrelatively loose-material, usually in the form of a layer covering aparticular area, and to compact that material into a more dense mass orbody. The machine is capable of effectively compressing variousmaterials, such as fill dirt or other fill materials, paving materials,such as various bituminous mixes, and many other materials.

Many material compacting machines have been provided in the past. Onegeneral type of machine has comprised a supporting vehicle frame mountedon wheels for movement over the surface to be compact-ed. Such a machineusually has an impactor or compactor blade mounted on the frame forvertical movement with a tamping action into the relatively loosematerial over which the vehicle moves. The compacting movement of theblade is accomplished by a drive motor on the frame, usually of theinternal combustion type, which is connected by a driving connection tothe blade. The most serious defect of prior art machines is that theyhave not been dynamically balanced which results in excessive vibrationand shock. Also, they have not been designed to provide adequateprotection of the driving motor from the serious shocks created by therepeated blows of the compacting blade with the surface which it iscompressing. The shocks created by these blows in prior art machines andthe shocks and vibrations due to the imbalances therein are transmittedback to the frame and the driving motor which it carries causing quickfailure or maladjustment of the motor and especially of its moresensitive parts such as the carburetor, timer and ignition systems, etc.

My invention provides a machine which is carried on a wheeled vehiclefor movement over the surface to be compacted in which the impactor orcompactor blade is driven by an internal combustion engine but in whichthe impactor blade is so supported on the frame and driven by the enginethat the engine is protected from shock developed by the impactingcontact of the blade with the material being compacted. Furthermore, themachine of my invention is so designed that it is dynamically balancedto reduce shock and vibration to the very minimum.

Various other objects and advantages will be apparent as thisdescription progresses.

In the accompanying drawings, I have illustrated a preferred embodimentof my material compacting machine and in these drawings:

FIGURE 1 is a side elevational view, partly cut away, illustrating theentire machine, including a riding sulky. FIGURE 2 is a plan view of themain part of the machine taken from the position indicated at line 22 ofFIGURE 1.

FIGURE 3 is an enlarged transverse vertical sectional view taken alongline 33 of FIGURE 1.

FIGURE 4 is a front elevational view of the machine, partly cut away,taken from the position indicated at line 4-4 of FIGURE 1.

FIGURE 5 is an enlarged vertical sectional view taken along line 55 ofFIGURE 1.

FIGURE 6 is an enlarged vertical sectional view taken along line 6-6 ofFIGURE 1.

FIGURE 7 is an enlarged horizontal sectional view taken along line 7-7of FIGURE 1.

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FIGURE 8 is a schematic side elevational view illustrating the movementof the compactor blade through several successive positions.

FIGURE 9 is a similar view illustrating movement of the compactor bladethrough other successive positions.

With particular reference to the drawings, the vehicle of this inventionis shown in FIGURES 1 and 2 as comprising a main frame 10 which ispreferably in the form of a heavy casting but which could be fabricatedfrom various steel members. The frame is carried by means of two supportand traction wheels 11, preferably of the pneumatically tired type,which are disposed at opposite sides of the frame in vertical planesparallel to the upright sides of the frame. These wheels 11 are carriedon the opposite ends of an axle 12 which project in opposite directionsout through the sides of the frame 10 from a differential unit 13supported centrally of the frame at the lower side thereof. Locatedbehind the differential unit and, in fact, combined therewith is themultispecd reversible transmission 14. This transmission is controlledby an upstanding shaft which has a single control handle 15 keyed on itsupper end and swingable in either direction to set the transmission forforward or reverse drive at a selected speed. To facilitate steering ofthe machine, each Wheel has a brake unit 16 associated therewith andeach brake unit is controlled by means of a control handle 17 located atthe rear of the frame and connected to an associated push-pull flexiblecontrol shaft at the respective side of the machine.

Mounted on the forward portion of the frame It) at the upper sidethereof is the drive motor 20 Which is preferably an internal combustionengine which has the gas tank at it upper side indicated at 21.. Theengine drives a generator 22 which is mounted thereon, the drive beingby means of a belt drive 23. The engine 24 also drives the transmission14 through a belt drive 24 (FIGURE 2) and a clutch 25 carried by atransversely disposed clutch shaft 26 which is located behind the engine20 on the upper portion of the frame 10. A chain and sprocket drive 27runs from the clutch 25 downwardly and rearwardly to the input shaft ofthe transmission 14. The clutch shaft 26 also has mounted thereon asecond clutch 28 which, through a sprocket and chain drive 29, drives aneccentric shaft 30 to be described in detail later. The clutches 25 and28 are controlled by laterally extending links 31 and 32, respectively,which are, in turn, controlled by the respective clutch levers 33 and 34which extend upwardly and rearwardly over a main handle structure. Thishandle structure is rigidly secured at its lower and inner or forwardend to the frame 12 and is used in steering and handling the machine. Ifdesired, a suitable sulky 36 (FIGURE 1) may be hitched to the rear endof the frame It at 37 and may carry a seat 38 which will position theoperator properly relative to the various control handles at the rear ofthe frame It The eccentric shaft 30, previously referred to, is part ofwhat might be termed the impacting unit as distinguished from thevehicle so far described. This impacting unit may be designatedgenerally by the numeral 40 and is so supported at the forward end ofthe frame 19 that it will prevent the transmission of most of the shocksfrom the impacting or compacting operation to the frame Ill and theengine 20 and associated parts carried thereby. Also, it issubstantially dynamically balanced in itself so as to prevent thedevelopment of excessive vibrations and resulting shock.

The unit 40 comprises the compacting shoe or blade 41 which ispreferably formed of steel and extends transversely completely acrossthe machine in front of the frame 10 and laterally beyond the wheels 11.It is formed to provide a flat, final impacting surface 42 ofsubstantial extent, in a forward and rearward direction, together with ajoining forward beveled surface 43 and a rearward beveled suface 44.Thus, regardless of the direction of movement of the machine, a beveledsurface 43 or 44, will gradually compress the material until it isfinally compacted by the surface 4-2 which follows the respectivebeveled surface as it advances into the material to be compacted.

The blade 41 is rigidly carried on the lower ends of a pair of laterallyspaced, parallel, heavy rigid arms 45 which depend from the shaft 30.The upper end of each arm 45 rotatably receive the associated outerreduced eccentric end or stub shaft 46( FIGURE 3) of the shaft 36. Thisconnection includes a self-aligning ball-bearing 47. Thus, theeccentrics 46 of the shaft are journaled for rotation in the upper endsof the arms 45 and on an axis that is at a higher level than the blade42 and parallel thereto. The shaft is driven by means of the flexiblechain drive 29, previously described, which permits bodily verticalmovement of the shaft. Towards its outer ends, the shaft 30 carries theweights 56 which are unbalanced and are preferably in the form of.eccentric flywheels which are flattened or have a segment removed toprovide a flat peripheral edge portion 51. Each weight 50 is keyed onthe shaft 30 with its heavier portion diametrically opposite theassociated eccentric 46 and with its flat edge 51 at the same side ofthe axis of the shaft as the eccentric 46. The eccentric weights 50 aredesigned to dynamically balance the effect of the eccentrics andassociated parts.

The unit 49 i supported for vertical movement in a substantially uprightplane transversely across the frame and spaced forwardly slightlythereof. This plane will be substantially perpendicular to the surface Sover which the wheels 11 roll it the frame is held in a normalhorizontal position by the handle 35 by pivoting it about the wheel axle12. This plane will be substantially parallel to the plane of theforward edge of the frame It) and it will be prevented from tiltingsubstantially from this plane by means of a linkage system which is asubstantially parallel linkage system but permits a slight rockingaction of the blade 41 due to the eccentric connections 46 of the shaft30 and the arms 45.

The parallel linkage for connecting the compacting unit 46 to the mainvehicle frame 10 comprises a pair of lower tie-links 52 and a pair ofupper supporting arms or links 53. The links of each pair extendlongitudinally, rearwardly and forwardly, in laterally spaced, parallelrelationship at the outer sides of the frame 10. The links 52 and 53 atthe respective sides are located at different levels. All the links arepivotally connected at their rear ends to the frame 10 and at theirforward ends to the unit 40. All the rear pivots are in a commonvertical plane transversely of the frame It and all the forward pivotsare in common vertical plane transversely and forward of the frame 10.Thus, the forward end of each tie-link 52 is pivoted on an axis 54,transversely parallel and slightly above the blade 41, adjacent anassociated arm 45. It will be noted that the lower end of each arm 45 isrigidly connected to the blade 41 by a pair of bolts 55 (FIGURE 1) toprevent tilting of the blade relative to the arm. Above this connectionis the pivot axis 54 which includes a rod 56 (FIGURE 4) extendingtransversely between the arms 45 and having reduced ends extendingthrough aligning openings in the arms. The forward ends of the links 52carry spacer collars 57 which engage at their inner edges shoulders onthe 7 rod 56 and at their outer edges spacer collars 58 provided on therod 56 between the respective arms 45 and the link collars 57. The rearends of the links 52 are pivoted on an axis 59 (FIGURE 1), transverselyof the frame 10 at its lower side. The pivot structure at this axis isillustrated best in FIGURE 7 and comprises a pivot bolt 60 carried byeach side wall of the frame and projecting laterally outwardlytherefrom. The adjacent forward end of the link 52 is provided with acollar or socket portion 61 in which a pivot bearing and cushioningcollar unit is disposed. This collar unit comprises a heavy collar 62 ofcompressible resilient rubber or other cushioning material fitted intothe socket 61 and an inner metal sleeeve 63 rotatably receiving the bolt60, the sleeve having flanged ends to keep the collar 62 axially inposition. Thus, I not only provide a pivot structure at this axis 59 butalso a cushioning structure substantially to prevent transmission ofshock through the links 52 to the frame it).

As shown best in FIGURES 3 and 4, the forward end of each arm 5'3 isrotatably connected to the shaft 30 and is located axially between theweight 50 at that end and the eccentric 46. Thus, the outer or forwardend of each arm 43 is provided with a socket 66 in which a self-aligningball-bearing 65 is disposed. This bearing 65 is provided with aperipheral flange 67 which may be bolted by bolts 68 to the arm 53around the socket 66. Thus, the main part of the shaft 30 is rotatablymounted. in the bearings 65 carried by the respective arms 53.

The rear ends of the arms 53 are pivoted for swinging movement about anaxis 70 (FIGURE 1) at the upper side of the frame 10. Each arm 53 isconnected to the frame it} by a pivot and cushion structure of the typeshown in FIGURE 6. The pivot includes a pivot and clam bolt 71 extendinglaterally outwardly from the frame 10 and which carries a relativelyheavy resilently compressible collar 72 of rubber or the like. Thiscollar is clamped in position by a clamping nut and collar 73 asindicated so that there is no metal-to-metal contact and the arm 53 iscushioned from the frame 10 by the compressible member 72. Thus,cushioning pivots are provided at the rearward ends of the respectivearms 53 to permit vertical swinging thereof but to prevent transmissionof shocks through the arms to the frame It To limit vertical swingingmovement of the arms 53 as a reaction to the impacting action of theblade 41, piston type shock absorbers 86 are provided below the frontend of each arm 53. It will be noted best in FIG- URE 1 that each shockabsorber 86 is pivoted at 81 at its upper end to the arm 53 just behindthe shaft 30 and is rigidly connected at its lower end as at 82 to theframe 10. The details of each of these shock absorbers is illustratedbest in FIGURE 5 where it will be noted that the pivot 81 is provided bya pin which passes through a U-shape clevis that slips upwardly over thelower edge of the arm 53 and is formed on the upper end of a cylindricalhousing of the shock absorber. Within this housing is a sleeve 90 ofcompressible resilient material having inner and outer metal sleeves 83and 84, re-

spectively. The outer sleeve 84 is fixed axially in the housing, forexample, by press-fitting. A rod 85 passes downwardly through the innersleeve 83 and its lower threaded end is adjustably anchored to a lug 86extending outwardly from the side of the frame 10 by means of the nuts87 above and below the lug. The sleeve 83 and associated parts are fixedaxially on the rod 85 by the fixed head 88 on the upper end of the rodand the adjustable nut 89 threaded on the rod below the sleeve and inclamping engagement therewith. The shock absorber units 8% may beadjusted to vary the vertical position of the blade 41 relative to theframe 10. This is accomplished by adjusting the nuts 82 on the threadedportions of the respective rods 65 and thereby varying the verticaldistance between the pivots 81 and the lugs 86.

In the operation of this machine, the engine 20 may be started by asuitable starter unit (not shown). This will cause the drive 23 to drivethe generator 22 and the drive 24 to drive the clutch shaft 26. Theclutches 25 and 28 may be selectively operated. If the clutch 25 isactuated by means of the handle 33, the transmission 14 will be drivenalong with the differential unit 13 which it drives. This, in turn, willdrive the wheels ill. The brakes 16 may be selectively actuated toretard either of the wheels 11 to aid in steering the machine. Thetransmission 14 may be set by operation of the handle 15 for forward orreverse drive at a selected speed. At this time, the machine will movein the desired direction at the selected speed and the weight shaft 30will not be driven. Therefore, the shoe or blade 41 will not be exertingits impacting action. However, by actuating the clutch 28, the shaft 30may be caused to rotate. This then will produce vertical impacting orcompacting movement of the blade 41. It is possible to release theclutch and actuate only the clutch 28 to drive the shaft 30 while themachine is stationary since the drive to the wheels 11 is interrupted.

When the shaft 30 is driven by means of the chain drive 36}, it rotatesin the bearings 65 in the arms 53. This causes the opposed eccentrics 46to revolve about the axis of the shaft 30 and, thus, produces movementof the arms 45 and the blade 41 carried thereby. The movement of theblade 41 is mainly vertical, to obtain a pounding or impacting action,due to the provision of the linkage which is provided by the lower links52 and the upper links 53. This linkage is substantially parallellinkage but is moved out of parallel at times to the extent of theeccentrics 46 being offset from the axis of the shaft 30. Also, becauseof these eccentrics there is a rocking movement of the arms 45 about thepivot axis 54 which provides a slight forward and rearward component ofmovement to the blade during its vertical movement. This is apparentfrom schematic FIGURES 8 and 9 where the blade 41 is shown moving fromits lower position D, through the successive positions A, B and C,brought about by the eccentrics 46 revolving about the axis of the shaftto successive 90 angular positions indicated by corresponding letters A,B, C and D. When the im pacting surface 42 of the blade 41 is moved intocontact with the surface to be compacted, a reaction is set up whichtends to move the entire unit vertically. However, this reactivemovement is limited by the shock absorbers 80 which tie the arms 53flexibly to the frame 10. Vertical movement of the arms 53 is permittedbut only to a limited extent by the shock absorbers 80. This movement isproduced by vertical flexing of the resilient sleeve 90. Thus, the bladewill produce successive impacting blows on the surface to be compactedand resulting vertical reactive movement of the arms 53 will be limitedby the shock absorbers 8%. These shock absorbers, as indicated, may beadjusted to locate the blade 41 at an initial predetermined levelrelative to the frame It As the arms are moved vertically by theeccentrics 46 to move the blade 41 vertically, the arms are also rockedby the eccentrics forwardly and rearwardly about the axis 54 whichresults also in a forward and rearward movement of the blade during itsvertical pounding movement. This produces a wiping or agitating actionon the material as it is being compacted which aids in the compaction.The blade will, therefore, as indicated in FIG- URES 8 and 9, advanceinto the loose material, gradually wedge it under the surface 43 andcompact it under the flat surface 42 which will be rocked about the axis54.

The impacting unit 40 is dynamically balanced to reduce to a minimum thevibrational effect of the vertical movement of the blade 41 by theeccentrics 46. This is accomplished by means of the pair of eccentricweights previously described. Each of the weights is fixed on the shaft39 to place its center of gravity diametrically opposite the associatedeccentric 46. Thus, during the impacting movements of the blade 41created by the eccentrics 46, the weights 50, being of appropriatedesign and arranged as indicated, cancels out or substantiallyeliminates vibration and shock which would otherwise be created by thevertical reciprocating movement of the blade 41 and arms 45. In effect,the shaft 36 is maintained in a position as a freely suspended body andthe eccentrics 46 impart the necessary displacement to the blade 41because of the shock-absorber connection to the main frame. Any shockwhich does result from the impacting action will not be transmittedreadily to the frame 10 and the engine and associated parts carriedthereby due to the provision of the cushioning units at the pivot axes58 and 70.

It will be apparent that this invention provides a machine whichcomprises mainly a wheeled frame that moves along the surface to becompacted and carries the driving motor or power unit of the machine. Atthe forward end of this vehicle unit there is suspended the impactingunit in such a manner that it is substantially balanced and is soconnected to the vehicle frame that any excessive shocks produced duringthe impacting action will not be transmitted to the vehicle frame andthereby damage the the driving engine and associated parts.

It will be apparent that many of the advantages of this machine havebeen discussed above and others will be readily apparent.

According to the provisions of the patent statutes, the principles ofthis invention have been explained and have been illustrated anddescribed in what is now considered to represent the best embodiment.However, it is to be understood that, within the scope of the appendedclaims, the invention may be practiced otherwise than as specificallyillustrated and described.

Having thus described my invention, what I claim is:

1. A compacting machine comprising a vehicle movable over the materialto be compacted, a compacting unit supported from the vehicle andincluding a material-contacting blade, means for suspending said unitfrom the vehicle for vertical movement to cause said blade to movevertically with a compacting action, means for producing such movement,said means comprising a shaft having eccentric ends disposed in bearingsin support arms upstanding from said blade and forming part of saidsuspending means, means for driving said shaft, said shaft carryingweight means for substantially dynamically balancing the forcesresulting from vertical movement of said blade and arms created by saideccentric shaft ends.

2. A compacting machine according to claim 1 in which said suspendingmeans includes suspending arms pivotally connected to said vehicle forvertical swinging movement, said suspending arms carrying bearings inwhich said shaft is supported for rotative movement, and yieldable meansconnecting said arms and said vehicle for permitting limited verticalswinging movement under control.

3. A compacting machine according to claim 2 in which said shaft drivingmeans comprises a power source on the vehicle; and a flexible drivebetween said power source and said shaft for permitting the verticalmovement of the unit relative to the vehicle.

4. A compacting machine according to claim 3 in which said yieldablemeans comprises shock-absorbing members.

5. A compacting machine according to claim 4 in which each of saidshock-absorbing members comprises a flexible sleeve connected betweeneach of said suspending arms and said vehicle frame at vertically spacedconnecting points.

6. A compacting machine according to claim 5 in which the distancebetween said connecting points is vertically adjustable.

7. A compacting machine according to claim 2 in which said suspendingarms are pivotally connected to said vehicle by pivots includingyieldable cushioning means for reducing transmission of shock from thearms to the vehicle.

8. A compacting machine according to claim 7 including means forlimiting tilting of said blade, said means comprising links pivotallyconnected to said blade support arms at a level between said blade andsaid shaft, said links being also connected to said vehicle by a pivotalconnection at a level below the pivotal connection of said suspendingarms to the vehicle to permit vertical swinging of the links.

9. A compacting machine according to claim 8 in which the pivotalconnection of each of the links to the vehicle includes a yieldablecushioning means for reducing transmission of shock from the links tothe vehicle.

10. A compacting machine comprising a vehicle movable over the materialt-o be compacted and comprising a frame supported on wheels, a powerunit supported on the frame for driving elements of the machine, acompacting unit supported from the vehicle and including amaterial-contacting and compacting blade extending transversely of thevehicle in front of said Wheels, means for suspending said unit from thevehicle frame in front of the frame for vertical movement to permit saidblade to move vertically with a compacting action, said means includinglaterally spaced support arms, substantially parallel linkage pivotallyconnected between said support arms and said vehicle frame forpreventing substantial tilting of said blade during its verticalmovement including upper support links and lower tie links, flexibledriving means connected between said power unit and said compacting unitto cause vertical movement of the latter, said parallel linkage alsoincluding cushioning means for substantially preventing transmisison ofexcessive shock from the compacting blade to said vehicle frame and thepower unit carried thereby, a shaft rotatably supported by said uppersupport links and provided with axially spaced eccentrics rotatablysupporting said support arms, said shaft carrying weight means forsubstantially dynamically balancing the forces resulting from verticalmovement of said blade and associated linkage and flexible driving meansconnected between said power unit and said shaft to cause verticalmovement of said blade.

11. A compacting machine according to claim 10 in which said eccentricson the shaft comprise stub-shaft ends displaced from the axis of theshaft, said weight means comprising weights fixed to the shaft andhaving heavier portions diametrically opposed to said stub-shaft ends.

12. A compacting machine according to claim 11 in which a pair of saidarms are provided and are disposed in laterally spaced relationship andrigidly secured to said blade in upright position, said eccentric weightshaft 8 being mounted in said upright arms in substantially parallelrelationship to said blade by said stub-shaft ends.

13. A compacting machine according to claim 12 in which said upper andlower links are pivoted respectively at their forward ends to saidupright arms and at their rear ends to said vehicle frame by pivotstructures which permit verical swinging movement of said links, saidpivot structures on each of said links including said cushioning meansin the form of cushioning collars coopearting with a pivot pin.

14. A compacting machine according to claim 13 including shock absorbersconnected between each of the upper links and said vehicle frame, saidshock absorbers comprising a yieldable sleeve connected respectively tosaid upper links and said vehicle frame.

15. A compacting machine according to claim 10 including a combineddifferential and transmission mounted on said vehicle frame, said wheelsbeing carried by axles extending from said differential, a clutch shaftdriven by said engine, and a drive from said clutch shaft to saidtransmission and including a selectively operable clutch.

15. A compacting machine according to claim 15 in which said flexibledriving means includes a drive chain between said clutch shaft and saideccentric shaft carried by said compacting unit, and including a clutchselectively operable to drive said weight shaft from said clutch shaft.

17, A compacting machine according to claim 16 including brakesassociated with each of said wheels and selectively operable.

References Cited UNITED STATES PATENTS 2,009,542 7/1935 Day 94-48 X2,333,041 10/ 1943 Poulter.

2,453,510 11/1948 Jackson 94-48 2,633,781 4/1953 Day 94-48 2,644,3797/1953 Lowe 94-48 2,687,071 8/1954 Day 94-48 2,884,842 5/1959 Schmitz94--49 JACOB L. NACKENOFF, Primary Examiner.

1. A COMPACTING MACHINE COMPRISING A VEHICLE MOVABLE OVER THE MATERIALTO BE COMPACTED, A COMPACTING UNIT SUPPORTED FROM THE VEHICLE ANDINCLUDING A MATERIAL-CONTACTING BLADE, MEANS FOR SUSPENDING SAID UNITFROM THE VEHICLE FOR VERTICAL MOVEMENT TO CAUSE SAID BLADE TO MOVEVERTICALLY WITH A COMPACTING ACTION, MEANS FOR PRODUCING SUCH MOVEMENT,SAID MEANS COMPRISING A SHAFT HAVING ECCENTRIC ENDS DISPOSED IN BEARINGSIN SUPPORT ARMS UPSTANDING FROM SAID BLADE AND FORMING PART OF SAIDSUSPENDING MEANS, MEANS FOR DRIVING SAID SHAFT, SAID SHAFT CARRYINGWEIGHT MEANS FOR SUBSTANTIALLY DYNAMICALLY BALANCING THE FORCESRESULTING FROM VERTICAL MOVEMENT OF SAID BLADE AND ARMS CREATED BY SAIDECCENTRIC SHAFT ENDS.